Machine tool transmission and control mechanism



L. H. BLOOD 2,119,902

MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM June 7, 1938.

Filed Sept. 27, 1934 6 Sheets-Sheet l g a 2g MFMHMMMFH i H. BLOOD2,119,902

MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM June 7, 1938.

Filed Sept. 27, 1954 6 Sheets-Sheet 2 Fly? 3 rwa/who'n (011/5 /1 31.0017

June 7, 1938. I H BLOOD 2,119,902

MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM Filed Sept. 27, 1934 6Sheets-Sheet 5 June 7, 1938. L. H. BLOOD 2,119,902

MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM Filed Sept. 27, 1934 6SheetsSheet 4 Fgy. 9 mm;

lows h. BL 00]! June 7, 1938. H BLOOD 2,119,902

\ MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM Filed Sept. 27, 1934 6Sheets-Sheet 5 June 7, 1938. l H BLQQD MACHINE TOOL TRANSMISSION ANDCONTROL MECHANISM Filed Sept. 27, 1934 6 Sheets-Sheet 6 /0/ /?4 m3} v "IUNITED STATES PATENT OFFICE MACHINE TOOL TRANSMISSION AND CON- TROLMECHANISM Louis 112 Blood, Cincinnati, Ohio, assignor to The CincinnatiMilling Machine Company, Cincinnati, Ohio, a corporation of OhioApplication September 2'1, 1984, Serial No. 745,773

1': Claims. (01. 60-52),

This invention relates to machine tools and Figure 7 is a sectionthrough the valve mechamore particularly to improvements in thetransnism as viewed on the line 'I- of Figure 4. mission and controlmechanism thereof. Figure 8 is a section on the line 8 -8 of Figure 4.

One of the objects of this invention is to pro Figure 9 is a sectionsimilar to Figure 8 but with vide a transmission which is hydraulic innature the valve plungers shifted to a rapid traverse 5 but which may beeasily and readily adjusted in position.

a similar manner to mechanical transmissions to Figure 10 is a partiallydiagrammatic view yield a plurality of feed rates which are in steppedshowing the arrangement of parts for yielding the relation and thereforesimilar to those yielded by lowest feed rate of which the transmissionis pos- 10 variable speed gear transmissions. sible. 10 Another objectof this invention is to pro- Figures 11 and 12 are views similar toFigure 10 vide in combination with a variable speed hybut with the partsshifted to other positions to draulic transmission in which variablerates are yield additional representative feed rates.

obtained by selectively adding or subtracting the Figure 13 is a viewshowing the manner of con- I5 flow from one or more of a plurality ofpumps of necting the hydraulic unit to the operating cylina singleunitary control for determining the der and the pick feed cylinder.pumps to be actuated, and the manner in which Figure 14 is adiagrammatic view of the hythose pumps are to be connected with the maindraulic circuit. I supply line. Figure 15 is a section on line l5l5 ofFigure 1.

A further object of this invention is to provide Although this inventionhas numerous other 20 in a transmission of the class described apreapplications, it has been exemplified in connecselective means fordetermining the number of tion with a shaping machine in which a repumpsto be actuated in order to'yield a desired ciprocable member such as thetool slide l5, as rate and subsequently actuated means for simulshown inFigure 1, is moved in one direction at a taneously coupling the selectedpumps for power prescribed feed or cutting rate and returned in 25actuation. the opposite direction at a quick traverse rate.

Other objects and advantages of the present The slide l5 may be providedat one end with invention will be readily apparent by reference tosuitable conventional means for supporting a cutthe followingspecification considered in conjuncting tool l6 for movement relative toa work suption with the accompanying drawings illustrative port H. Theslide l5 may be provided with ways 30 of one embodiment thereof, but itwill be under- H! by which the same is supported. and guided stood thatany modifications may be made in the for reciprocation relative to thefixed bed or supspeci fic structural details thereof within the scopeport l9 oi the machine. of the appended claims without departing from Asshown in Figure 13 the slide I5 may be reor exceeding thespiritof theinvention. ciprocated by means of an hydraulic motorcom- 35 Referring tothe drawings in which like referprising a cylinder 20 which is fixed inthe slide ence characters indicate like or similar parts: for movementtherewith and a differential pis- Figure 1 is an elevation of a machinetool emton 2| which is fixed to the support [9 by a piston bodying theprinciples of this invention. rod 22. The piston rod has a central bore23 40 Figure 2 is a section through the control mechthrough which fluidis admitted to the left end 40 anism as viewed on line 2-4 f Figure 1,of the cylinder for effecting feed rates and a Figure 3 is a section onthe line 3-3 of Figure 2. second longitudinal bore 24 through whichfluid is Figure 4 is a section on the line of Figure 2 admitted to theright hand end of the cylinder showing the arrangement of the valvingand the for effecting quick traverse return mov ments of controlmechanism the tool slide. Due to the large diame er of the Figure 5 isan expanded View showing the piston rod, it will be apparent that if thesame volume of fiuid is delivered per unit of time and. rangement oi thecam paths in the cam unit which controls the valves for cou 1m and unalternately to opposite ends of the cylinder, that i p g the advancingor feeding rate will be very much coup mg 6 My pumps n manne? t slowerthan the return rate. By means of this 50 crease or decrease the feedarrangement it is possible toutiliae the same Figure 6 is an expfmdedshowing the 091m pump for effecting a slow feeding rate and a paths inthe cam unit which determines the courapid return t pling of all theauxiliary pumps for actuation by An improved hydraulic circuit has beenpro- 5 the prime mover. vided for supplying fluid to the cylinder insuch 56 a manner-as to yield a plurality of forward feed ing rates aswell as a. quick traverse return rate and in whichthe feed rates may beselectively volumetric flows which, when adding to or sub-' tractingfrom the main flow, will increase or decrease the final rate in stepsabove or below said -intermediate rate.

Tothis end a main or principal constant displacement pump 25, as shownin Figure 14, is provided for delivering the main hydraulic flow to thecylinder which, when acting alone, will yield the intermediate feedrate. This pump has an intake 26 for withdrawing fluid from the mainreservoir 21 and a delivery pipe 28 through which fluid is forced at aconstant volumetric rate to the cylinder. Channel 28 may be connected toa conventional form of emergency relief valve 29 by means of which partof the fluid may be bypassed to reservoir through a channel 36 in caseof emergency.

The flow from the relief valve continues.

through line 3| to port 32 of a stop valve 33.

This valve, as more particularly shown in Figure '7, has a reciprocableplunger 34 on which is formed three spools 35, 36 and 31 which spoolsact when the plunger is in the running position as shownto'inter-connect port 32 with port 38 and also to connect port 39 withport 40. The plunger is pulled outward from position shown .by means ofa stop lever 4| which is pivotally mounted on the fixed pin 42 andoperatively connected by an elongated slot 43 formed in the lower endthereof with a fixed pin 44 in the end of plunger 34. From \this it willbe seen that counter-clockwise movement of the lever 4| will pull theplunger 34 toward the right until the stop 44' abuts the wall 45. Thismovement is sumcient to move the spools 35 and 36 to such a positionthat they will inter-connect ports 38 and 39 and simultaneously connectports 32 and 40 to reservoir.

The flow from port 38 will continue through an intermediate passage toport 46 of the rate and direction control valve 41. This valve has aplunger 48 through which the fluid passes to port 49 and channel 50, thechannel terminating in a port 5| of valve 52, This valve has a plunger53 in which is formed an annular groove 54 through which the fluidpasses when the valve is in the position shown in Figure 8 to the feedline 55. This feed line is connected to the end of the central bore 23of the piston rod, as more particularly shown in Figure 13. Operation ofthe pump 25 will therefore cause forward movement of the tool slide at adefinite predetermined feed rate because the pump 25 is a constantdisplacement pump and driven at a uniform rate.

As the cylinder advances relative to the piston rod, the fluid in theright end of the cylinder will escape through the bore 24 in the pistonrod nd the pipe 56 connected therewith as shown in Figure 13 to port 51of the rate and direction control valve. This port, as shown in Figure14,

is connected by the cannelure 58 of plunger 53 when the same is in thefeed position as shown in Figures 7 and 14 to the return port 59. Thisreturn or exhaust port permits the fluid to return to the main reservoir21.

When the tool slide has advanced a predeterfixed to the side of theslide l5, the trip dog will rotate a trip plunger 6| through the mediumof a trip lever 62 attached to the upper end of the plunger andextending into the path of the dog. The lower end of the plunger has anarm 63 secured thereto as shown in Figure 15 which carries a pin 64having a lost motion connection with a segment member 65. This lattermember in-v ter-meshes with a reciprocable rack bar 66. A spring presseddetent 6I inter-engages with suitable formed V-shaped indents in themember 63 to complete the firing in the well-known manner of load andfire mechanisms.

The rack bar 66 extends longitudinally of the machine as shown in Figure1 and has rack teeth 68 formed on the under side thereof forinterengagement with a segment 69 keyed to the 'inner end of shaft Iwhich has a manually operable lever II secured to the outer end thereof.This lever serves as a manual means for operating the detent mechanismand thereby manually controlling the reversing of the machine.

The rack bar 66 inter-meshes with a pinion I2 as more particularly shownin Figure '7, which pinion also inter-meshes with a plunger 13 of apilot valve I4. Attention is invited to the fact that the rack 66 andpinion I2 have been thrown up through an angle of 90 degrees for thepurposes of illustration because if" shown in a true position the pinionI2 would lie directly behind the plunger I3. The true relationship ofthese parts is shown in Figure 13.

The pilot valve I4 serves to control power shifting of the rate anddirection control valve. Power for this purpose is obtained from anaccumulator I containing a spring loaded plunger I6. The accumulator isloaded in the following manner. The port 46 in Figure 7, it will beremembered, is connected at all times to the main pump during operationof the machine, and therefore this port is always under pressure. Theport 46 is formed in the annular groove II circumscribing the sleeve I8which groove lies in the plane of a ball check valve I8, the fluidflowing past this valve escaping into the bore containing plunger I3.Since the flow of oil around the annular groove 11 is unaifected by theposition of the rate and direction valve plunger 48, the flow past thecheck valve will be continuous during operation of the main pump 25.This fluid passes through a port 80 in the pilot valve, which port iscontrolled by the spool 8| secured to the plunger I3. It will be notedfrom the position of the parts in Figure 7 that the port 80 is open asmall amount permitting fluid to flow into the cannelure 62 from whichit passes through the space formed by the flattened sides 83 of spool 8|to the port '64 of the accumulator. When the plunger I3 is in theprocess of moving from one extreme position to the other, the port 68 isclosed but the flattened sides 83 permit flow from the accumulator tothe cannelure 82.

The cylinder I4 which contains plunger I3 has a port 85 which isinter-connected with port 64 of the accumulator when the plunger is inthe position shown to permit passage of fluid to port 86 formed in theright hand end of the rate and direction control valve for shifting theplunger '48 to its extreme left position which may be termed the feedforward position. Upon operation of the trip plunger, the rack bar 66will, throughthe pinion I2, cause reciprocation of the plunger I3 toitsextreme left position, thereby incontains the plunger 53.

terconnecting port 84 of the accumulator with port 81 which admits fluidto the left end of the rate and direction valve, thereby shifting theplunger 48 to the right or to its rapid return position, which positionis shown in Figure 9. This will disconnect the port 46 from port 49 andcouple port 46 with port 51 and line 56 and thereby will connect thepump 25 for rapid return movement of the toolslide.

The plunger 48 has rack teeth 88 formed in the end thereof whichinter-mesh with a pinion 89 secured to the end of shaft 90. This shaft,as shown in Figure 8 has a second pinion 9| secured thereto whichintermeshes with rack teeth formed on the end of plunger 53. The purposeof this is that when the rate and direction control valve is shifted toits rapid traverse position, it will simultaneously cause shifting ofplunger 53 and thereby interconnect the line 55 with the reservoir. Thisis accomplished by providing an L- shaped passage 92 in the spool 93secured to the end of plunger 53. In order, however, to prevent all ofthe oil from draining out of the passage 55 during the rapid returnmovement, a spring pressed plunger 94 is provided which has a coneshaped end 95 adapted to inter-fit a cone-shaped counter-sink in the endof the sleeve 91 which I When the plunger 53 shifts to the positionshown in Figure 9, the plunger 94 will tend to close the escape of oilthrough the passage 92 and will act in a manner of a check valve wherebywhen the pressure in the line 55 drops below that suflicient to moveplunger 94 against the spring 98, the cone-shaped end 95 will shut oifthe further escape of oil. This will maintain the pipe 55 filled withoil at all times and prevent the accumulation of air in the hydraulicsystem.

Means have also been provided whereby each change in direction of thetool slide will operate a ratchet pick feed mechanism for translatingthe work slide laterally of the tool slide. To this end the pilot valvehas a pair of channels 99 and I connected to ports 85 and 81 so thatthese channels will be alternately under pressure as plunger 13 isshifted between its two positions. The channel 99 is connected to oneend of a cylinder IOI containing a piston I02 having a piston rod I03 onwhich is formed rack teeth I04 intermeshing with a pinion I05. Thispinion, as shown in Figure 1, is secured to the upper end of a splineshaft I06 which inter-engages a pinion I01 carried by the knee I08 whichin turn carries the work support. The pinion I01 inter meshes with arack bar I09 which is operatively connected through lost motion meanswith a ratchet lever IIO having a spring pressed ratchet pawl III whichinter-engages with teeth II2 formed on the wheel II3. From this it willbe seen that when the plunger 13 is shifted to the position shown inFigure '1 to cause aforward feeding movement,.that pressure is alsoadmitted to channel I00 which will shift the plunger I02 shifting ofplunger I02 and thereby moving the pawl to a return position preparatoryto. a new pick feed movement.

From the description thus far, only the means for obtaining one feedrate has been described which is that yielded by the pump 25 which maybe arbitrarily assumed, for purposes of description, as 40 feet perminute, and the means for increasing or decreasing this rate bypredetermined steps will now be described. This means Y comprises aplurality of auxiliary pumps such as H4, H and II 6 which may bearranged in the same manner as the drive shafts are shown in Figure 2.

For instance, the pump 25 is attached to the wall or partition H1 insuch a manner that the drive shaft thereof is connected to the end of ashaft I I8 anti-frictionally journaled in the casing and carrying afixed gear II9 which inter-meshes with a common drive gear I20. Thedrive gear I20 is keyed to a shaft I2I as more particularly shown inFigure 3, and has one end projecting beyond the wall of the casing forinter-connection as by an Olclham coupling I22 to a prime mover I23mounted on a bracket I24 at the rear of the machine as shown inFigure 1. The pumps I I5 and II 6 as shown in Figure 3 are alsosupported on the partition II1 with their shafts projecting therethroughand operatively connected to drive shafts I25 and I26 respectively. Thepump H4 is also supported on the partition I'I1 as shown in Figure 4 andis connected for actuation by a shaft I21, Figure 2. These pumps are ofdifferent capacity whereby they may be combined in various combinationswith the main pump to produce a sufficient number of steps orgraduations in the feed rate and the total range of the feed rate willdepend upon the individual capacities chosen for the auxiliary pumps. Asillustrative of suitable capacities, the pump 6 may be considered ashaving a capacity sufiicient to yield a feed rate of 8 feet per minute;the pump I I5, a feed rate of 16 ft. per minute, and the pump II4 a feedrate of 40 ft. per minute. By coupling pumps H5 and H6 for subtractionof flow from the main line, a minimum feed rate of 16 ft. per minute maybe obtained and if all of the pumps are connected for delivering fluidinto the supply line a maximum feed rate of 104 ft. per minute may beobtained.

It will be noted from Figure 4 that all of the pumps and valve mechanismare mounted in a container which also serves as a reservoir and thiscontainer may be inserted into or withdrawn from the body of the machineas a unit. This eliminates the necessity for return connections.

such as pipes from the exhaust ports of the various valves.

A control mechanism has been provided for not only coupling anduncoupling the various auxiliary pumps for actuation by the prime mover,but i 'these pumps will be rendered ineffective. To this end a handwheel I28 is secured to the end of a shaft I29 rotatably journaled inthe wall I30 of the container and having keyed to the inner end thereofa bevel gear I3I which intermeshes with a similar bevel gear I32. A dialI33 is also secured for rotation with the hand wheel and carriessuitable numerals such as I 34 which cooperate with a fixed pointer I35to indicate the feed rate setting of the mechanism. From this it will beseen that by rotation of the hand wheel the entire series of feed ratesmay be successively obtained.

The bevel gear' I 32 is mounted for free rotation on the shaft I26 asshown in Figure 3, and

this gear has integrally formed therewith a'spur gear I35 whichintermeshes with a spur gear I31 formed integrally on the end of a camdrum I38,

.Figure 4. -This cam drum is mounted for free rotation on a shaft I39and is also axially movable on this shaft by means of a lever I40 whichis fixed to the end of a rotatable shaft I. A spring I42 normally holdsthe cam drum in the position shown in Figure 4 and with the teeth of thespur gears I35 and I31 intermeshed.

The shaft I4I projects through the front wall of the unit and has anL-shaped lever I43 secured thereto, the end of one arm of whichconstitutes a hand grasp I44 and the end I45 of the other arm of thelever being V-shaped to interfit with a plurality of V-shaped indentsI45 which are equal in number to the number of feed rates. This leveracts as a sort of interlock between the hand wheel and the cam drum insuch a way that the cam drum must be shifted inorder to permit rotationof the hand wheel and in shift-4 ing the cam drum the various pump drivegears are disconnected from the prime mover so as to reduce the frictionand load on the hand wheel during rotation thereof. The spring I42 hasthe dual function of shifting the cam drum to reengage the selectedgears and also operates through the lever to interconnect the detentsand act as a means for holding the hand wheel ,in a selected positionand to prevent rotation thereof until the hand lever is shifted.

The function of the cam I38 is to connect the auxiliary pumps to theprime mover only when they are actually utilized to vary the feed rate.thereby preventing needless circulation of the oil and consequentheating thereof resulting in an eflicient and economical structure. Tothis end the various pumps are provided with individual shiftable gearsfor connecting and disconnecting the various pumps with the common drivegear I20. For instance, the shaft I25 shown in Figure connecting anddisconnecting pump II; the shaft I25 has splined thereon a shiftablegear I48 for connecting and disconnecting pump H5; and shaft I21 hassplined thereon a shiftable gear I49 for connecting and disconnectingpump H4. The means for shifting these gears comprises a shifter fork I50engaging an annular groove I5I in gear I41 and supported for slidingmovement on a shaft 152.. The fork also has integral therewith afollower I53 adapted to ride in a cam path I54 formed on the cam drumI31.

' The gear I49 is shifted by a fork I55 mounted for sliding movement ona rod I55 and having a follower I 51 which engages a cam groove I50.

Likewise, the gear I40 is -shifted by a fork I50 .low rs for the variousintermediate rates. In

the owest rate position it will be noted that the foil wer I51 is in aposition to disconnect gear I49 from the common drive gear I20 while thefollowers I53 and I 5| are in a position to connect gears I41 and I40respectively to the common drive gear. In other words, the ordinatesI55, I55 and I51 correspond to the engaged position of the gears and theordinates I50, I59 and gears.

In addition to providing for operation of the pumps only when needed,means have also been provided for determining whetherthe auxiliary pumpsH5 and H5 shall function in an additive or subtractive manner. In otherwords, each pump is provided with separate valve mechanisms I correspondto the disengaged position of the which may be adjusted to cause thepump to deliver into the main line or withdraw fluid therefrom. Thesevalvesare shown in Figures 10, 11 and 12 and the manner of operationwill now be described. I

The reference numeral I1I indicates one of I tion which the plunger I12may assume is shown I in Figure 12 in which the cannelure I13interconnects ports I14 and I15.

A second plunger I16 is slidably mounted in the valve and has acannelure I11 formed therein which, as shown in Figure 10, willinter-connect ports I10 and I19 while upon movement to a second positionas shown in Figure 12 the port I15 will be closed and the port I19 willbe connected to reservoir. A common channel I00 serves to connect thesevalves to port 40 of the stopvalve 33. The port I14 is connected throughbranch IOI to channel I00 and the port I15 is connected through channelI02 to the delivery port I03 of the auxiliary pump, such as 5. Port I18is connected by branchline I04 to the common channel I00 and the portI19 is connected by the'branch ne I05 to the intake port I 85 of theauxiliary p p II5. In the position of the valve plungers associated withpump H5 in Figure 10, the pump is so connected that it will withdrawfluid from channel I80; In other words, the fluid will flow from channelI00 through branch I84, port I10, cannelure I11, port I19, branchI0'5.to the intake port m of pump II5 and-be forced out through thedelivery tion shown in Figure 11 while the plunger I12 remains in thesame position, it will be seen that -both ports I14 and I10 aredisconnected from pump H5 so that although this pump-is idle anddisconnected from the commonv drive gear, still the pressure of thefluid inchannel I80 cannot escape through the pump in any man nerwhereby this pump is rendered ineffective. If the plunger I15 is nowmaintained in the sameposition and the plunger I12 is shifted to theright, the port I14 will be interconnected with port I15 and the portI10 will be connected to reservoir; and since this valve is submerged inoil, as previouslyexplained, the intake side of pump II5 will withdrawoil from the reservoir through port I19, channel I05 and'intake port I05and force the fluid out through delivery port I03, channel I02, portI15, cannelure I13, port I14, branch IOI into the common line I80, thepump thereby acting to add fluid to the feed line.

In other words, in Figure 10 the pump H5 is shown connected to thecommon line I80 in a manner to subtract fluid therefrom; in Figure 11pump H5 is shown connected in such a manner that it is ineffective; andin Figure '12 the pump is shown connected in such a manner that it willadd fluid to the line I 80. The same conin the end of plunger 53 toreservoir.

nections can be made in connection with pump II6 so that furtherdescription thereof is not believed to be necessary. The pump H4 isutilized only for the purpose of adding fluid to the line, and thereforeis merely connected to the line through a check valve I81 so that whenthe pump is delivering, it will force fluid past the check valve; butwhen stationary, the check valve will prevent escape of fluid from lineI88 back through the pump.

The cam drum I88 shown rolled out in Figure 5 has cam grooves I89 andI98 for controlling the positioning ofthe plungers I16 and I12respectively for pump H6, and the cam grooves I9I and I92 forcontrolling the positioning of the plungers I16 and I12 for the controlvalve of pump H5. The actual arrangement of the cam grooves and plungerscontrolled thereby is shown in Figure 13 and to avoid misunderstandingin the interpretation of Figures 10, 11 and 12 which are somewhatdiagrammatic, the cam grooves I89 to I92 inclusive in Figure 5 must beconsidered as turned over in their individual positions because thevalves "I are on the right hand side of the cam drum, Figures 10, 11 and12, rather than on the left hand side as shown in Figure 13.

Cam drum I88 is mounted for free rotation on a shaft I93 and is providedwith spur gear teeth I94 on the end thereof for inter-meshing with thespur gear I36 whereby the drum I88 may be simultaneously rotated withthe drum I38 upon rotation of the hand wheel I28.

It will now be seen that when the feed rate is to be changed, that thelever I44is moved in a clockwise direction to release the hand wheel I28and shift the cam I38 against the resistance of spring I42 to therebymove all of the shiftable gears out of engagement with the gear I20 sothat the drums may be rotated with a minimum of friction. Rotation ofthe two drums will properly position the plungers of the control valvesIll and will also preselect the shiftable gears which are to be engagedwith gear I28.

The flow from line I88 passes through port 48 of the stop .valve to port39 by way of the cannelure I95, Figure '1, which is inter-connected byan intermediate passage to port I96 of the rate and direction valve.This valve has a spool I91 which is flattened out on the sides-to permitthe flow from port 46 to combine with the flow from port 96 before itpasses to the pipedelivery from the auxiliary pumps will pass through asecond L-shaped opening I99 formed Thus the main pump may be utilizedfor returning the slide at a rapid traverse rate and the auxiliary pumpsmomentarily connected to reservoir during this time.

It will thus be seen that an improved transmission and control mechanismof an hydraulic nature has been provided for the operation and controlof a machine tool slide.

What is claimed is: v

1. In a machinetool having a fluid operable motor for actuating a slidethereof, a first pump, and a channel for connecting'said pump to themotor, the combination of a plurality of auxiliary pumps for varying thequantity of flow in said channel including valve means fordeterminingthe pumps to be placed in communication with said channel, a commonactuating means for the pumps, and a control mechanism having a firstpart operable for determining the pumps to be actuated, and a secondmeans for conditioning the valve means of the actuated pumps wherebyonly the pumps that are placed in communication with said channel areactuated.

2. In a machine tool having a slide, a fluid oprality of auxiliarypumps, shiftable valve means for determining the auxiliary pumps to beplaced in communication. with said channel for varying the volumetricrate of flow therein, a prime mover, shiftable means for selectivelycoupling the auxiliary pumps to the prime mover, a first cam means forshifting said valve means, a second cam means for shifting said couplingmeans, and a control mechanism for actuating both of said cam means. I

3. In a machine tool having a fluid operable motor for effectingrelative movement between a tool and a work piece, and a pump fordeliver ing a constant flow to said motor, the combination of auxiliarymeans for adding to or subtracting from said flow including a pluralityof devices alternatively connectible for injecting,

fluid into the line or withdrawing fluid therefrom, power operable meansfor actuating said devices, and a control mechanism for determining saidalternative connections and the power actuation of the devic s utilized.

4. In a machine tool having a fluid operable motor for effectingrelative movement between a tool and a work piece, the combination ofmeans for actuating said motor at a plurality of feed rates including aplurality of constant displacement pumps connectible to the motor invarious combinations to yield a series of rates, a source of power,means to perselect the necessary pumps which will yield a given rate,valve means operable to connect the selected pumps with the motor, andmeans to connect said valve means for simultaneous adjustment with saidpreselecting means.

5. In a machine tool having a work support and a tool support, thecombination of hydraulic means for efiecting relative movement betweensaid supports including a fluid operable motor, a constant deliverysupply for said motor, a plurality of pumps, valve means for selectivelyconnecting said pumps for increasing or diminishing said supply,actuating means for the pumps, said valve means also being operable todisconnect one or more pumps from the main flow, a control for shiftingsaid valve means to either of its positions including means to couplefor actuation only the pumps that are placed in communication with saidmain flow by said valve means. I

6. In an hydraulic system for actuating a part,

- mover only the pumps that are valve-connected to the main flow.

'7.'In a machine tool having a slide, a fluid operable motor connectedthereto, a constant displacement pump and a channel connecting the pumpto the motor, the combination of a plurality of auxiliary pumps,shiftable valve means for determining the auxiliary pumps to be placedin communication with said channel for varying the volumetric rate offlow therein, a prime mover, shiftable means for selectively coupling,

the auxiliary pumps with the prime mover, a first rotatable camoperatively connected for shifting said valve means, a second rotatablecam operatively connected for shifting said coupling means, and amanually rotatable member operatively connected for jointly rotatingsaid cams.

8. In a machine tool having a slide, a fluid operable motor connectedthereto, a constant displacement pump and a channel connecting the pumpto the motor, the combination of a plurality of auxiliary pumps,shiftable valve means for determining the auxiliary pumps to be placedin communication with said channel for varying the volumetric rate offlow therein, a prime mover, shiftable means for selectively couplingthe auxiliary pumps with the prime mover, a

first rotatable cam operatively connected for shifting said valve means,a second rotatable cam operatively connected ,for shifting said couplingmeans, a manually rotatable member operatively connected for jointlyrotating said cams,

' and a dial associated with said member for indicating the feed rateseffected by the different positions of said cams.

9. In a machine tool having a slide, a fluid operable motor connectedthereto, a constant displacement pump and a channel connecting the pumpto the motor, the combination of a plurality of auxiliary pumps,shiftable valve means for determining the auxiliary pumps to be placedin communication with said channel for varying the volumetric rate offlow therein, a prime mover, shiftable gears for selectively couplingthe auxiliary pumps to the prime mover, afirst rotatable cam forshifting said .valve means, a second rotatable cam for shifting saidgears, a common rotator for said cams, and means for imparting an axialshift to the second cam before rotation -thereof whereby all gears willbe free during relative positioning thereof.

10. In a machine tool having -a slide, a fluid operable motor connectedthereto, a constant disaxial shift to the second cam to disconnect allgears --from the prime mover during rotation of the cam, and aninter-lock to prevent rotation of the second-cam until the same has beenaxially shifted.

11. In a machine tool having a slide, a fluid operable motor connectedthereto, a constant displacement pump and a channel'connectingthe pumpto the motor, the combination of a plurality of. auxiliary pumps,shiftable valve means for determining the auxiliary pumps to be placedin communication with said channel for varying the volumetric rate offlow therein, a prime mover, shiftable gears for selectively couplingthe auxiliary pumps to the prime mover, a first rotatable cam forshifting said valve means, a second rotatable cam for shiftingsaidgears, a common rotator for said cams, means for imparting an axialshift to the second cam to disconnect all gears from the prime moverduring rotation of the cam, and resilient means for efiecting a returnaxial shift of said cam to re-engage the selected gears with the primemover.

12. In a machine tool having a slide, a fluid operable motor connectedthereto; a constant displacement pump and a channel connecting the pumpto the motor, the combination of a plurality of auxiliary pumps,shiftable valve means for determining the auxiliary pumps to .be placedin communication with said channel for varying the volumetric rate offlow therein, a prime mover, shiftable gears for selectively couplingthe auxiliary pumps to the prime mover, a first rotatable cam forshifting said valve means, a second rotatable cam for shifting saidgears, a common rotator for said cams, means for imparting an axialshift to the second cam to disconnect all gears from the prime mover,resilient means for effecting a return axial shift of said cam toreengage the selected gears with the prime mover, and an interlockingmember operable by the return movement of the second cam for maintainingsaid cam means in any given rate position.

13. In a machin tool having a work support and a tool support, hecombination of hydraulic means for effecting relative movement betweenthe supports including a fluid operable motor, a

first constant delivery pump, a channel connect- I ing said pump to themotor, a second pump, valve means having portions selectively shiftablefor coupling the delivery of the second pump to said channel forincreasing the rate of said relative movement, or for connecting theintake port of the second pump to said channel for decreasing thedelivery to the motor and thereby the rate of said relative movement,said portions also being positionable for disconnecting said channelfrom;

a port associated with each plunger, and respectively connected totheintake and-delivery ports of said pump, a reservoir port connected witheach plunger, both of said plungers having a position forinter-connecting the pump ports to reservoir, means to shift one of saidplungers to connect the pump delivery port with said channel to increasethe feed rate or to shift the other plunger to connect the intake portof the pump with said constant volumetric source for supplying said.

motor including a delivery channel therefor, a

to the delivery side of said pump, and a second port connected to theintake side of said pump, a first valve plunger for connecting the firstport to said channel, and a second valve plunger for connecting thesecond port to reservoir to increase the volume delivered to said motor,means,

to, shift both of said valve means to reverse the connection of saidports respectively with respect to said channel and reservoir to therebydiminish the flow delivered to said motor, said plungers also beingpositionable to seal said channel from both of said ports whereby therate of operation of said motor will be determined by said constantvolumetric source.

16. In a machine tool having a work support and a tool support, thecombination of hydraulic means for efiecting relative movement betweensaid supports including a fluid operable motor, a supply channeltherefor, a, first constant displacement pump connected to said channelfor effecting a predetermined rate of operation of said motor, aplurality of additional pumps having predetermined difierent capacities,valve means having a first position to connect the pumps severally tosaid channel for diminishing the flow therein to provide a first seriesof feed rates, a second position for connecting the pumps severally forincreasing the flow in said channel to provide a second series of rates,and an additional pump selectively connectible in combination with theadditional pumps either jointly or severally to produce a third seriesof feed rates, a rotatable cam for positioning said valve means, a primemover, and a rotatable cam for selectively connecting with the primemover the pumps to be utilized. I

17. In a machine tool having a work' support and a tool support, thecombination of hydraulic ineans for eifecting relative movement betweenthe supports including an hydraulic motor connected to one of saidsupports, a channel connecting the pump to the motor, and means to varythe volume of fiuid delivered by said channel to the motor including asecond pump having intake and delivery ports and valve means forproducing three difierent operative effects of said additional pump uponthe flow in said channel whereby in one instance the additional pumpwill increase the flow in said channel; in a second instance it willdecrease the flow in said channel; and in a third instance it will notdisturb the flow produced in said channel by the first-named D p- LOUISH. BLOOD.

